EP2899427B1 - Transmission for a motor vehicle - Google Patents

Description

The invention relates to a transmission, in particular a multi-speed transmission, for a motor vehicle, comprising a housing, a drive shaft, an output shaft, at least two planetary gear sets, the first planetary gear set comprising a sun gear, at least one planet, a planet carrier and a ring gear, and a plurality of shift elements.

From the DE 10 2013 202 045 a group transmission of a motor vehicle has become known. The group transmission comprises a multi-stage main transmission and a range group subordinate to the main transmission in terms of drive technology. The range group is designed in a planetary design and comprises two coupled planetary gear sets, each with a sun gear, several planet gears carrying planet gears and a ring gear. The two planetary gear sets of the range group are arranged coaxially and axially staggered with respect to one another, the first planetary gear set being arranged axially between the main transmission and the second planetary gear set. The sun gear of the first planetary gear set is non-rotatably connected to the main shaft of the main transmission and thus forms the input element of the range group. The planet carrier of the first planetary gear set is rotatably connected to the ring gear of the second planetary gear set. The ring gear of the first planetary gear set is rotatably connected to the sun gear of the second planetary gear set. The planet carrier of the second planetary gear set is rotatably connected to the output shaft and thus forms the output element of the range group.

Furthermore, in the DE 10 2004 014 082 A1 discloses a double clutch transmission in planetary design. The double clutch transmission has four planetary gear sets, two frictional shift elements and several positive shift elements. The frictional shift elements are provided for connecting various power paths in a power flow of the planetary gear. The form-fitting switching elements are in turn provided for setting different gear ratios in the performance paths of the planetary gear. Furthermore, the frictional shift elements and the positive shift elements are between the shafts of the planetary gear sets, a housing or housing-fixed component of the planetary gear as well as a transmission input shaft and a transmission output shaft arranged that gear changes can be carried out without interruption of traction via the frictional shifting elements.

The disadvantage here is, among other things, that a pot penetration is required for actuation due to the internal switching elements. Furthermore, there are only six gears available in the dual-stage transmission described.

In the document EP 0 618 382 A1 discloses an auxiliary transmission assembly for a compound transmission, and more particularly, an improved auxiliary transmission assembly with a planetary gear set for defining selectable torque transmission paths between an input shaft and an output shaft of the auxiliary assembly.

It is therefore an object of the present invention to provide a transmission for a motor vehicle which enables easy access to shifting elements, has a high number of gears and is compact. In addition, it is an object of the present invention to provide an alternative transmission.

The present invention solves the problem with a transmission according to claim 1.

The invention also achieves the object with a motor vehicle, in particular with a passenger or truck, with a transmission according to one of claims 1 to 10.

Advantages here include that the majority of the shifting elements are easily accessible and, for example, for shifting forks is easily accessible from the outside. It is therefore not necessary to reach through the pot to actuate the corresponding switching elements. Further advantages are a compact design, small inertia masses and a power density due to the division over several planet gears. In addition, a sufficiently high number of gears can be represented with the transmission.

A torque or a rotational movement of a drive shaft, for example an internal combustion engine, is particularly preferably introduced into the transmission via the drive shaft.

In the following, a shaft is not only to be understood to mean, for example, a cylindrical, rotatably mounted machine element for transmitting torques, but rather also general connecting elements that connect individual components or elements to one another, in particular connecting elements that connect several elements in a rotationally fixed manner.

Two elements are particularly referred to as being connected to one another if there is a fixed, in particular rotationally fixed connection between the elements. In particular, such connected elements rotate at the same speed.

Two elements are referred to below as connectable if there is a detachable connection between these elements. In particular, such elements rotate at the same speed when the connection is established.

The various components and elements of the named invention can be connected to one another via a shaft or a connecting element, but also directly, for example by means of a welded, pressed or other connection.

A coupling is preferably to be understood in the description, in particular in the claims, as a switching element which, depending on the actuation state, permits a relative movement between two components or represents a connection for transmitting a torque. A relative movement is understood to mean, for example, a rotation of two components, the speed of the first component and the speed of the second component differing from one another. In addition, the rotation of only one of the two components is also conceivable while the other component is stationary or rotating in the opposite direction.

In the following, a clutch that is not actuated is to be understood as an opened clutch. This means that a relative movement between the two components is possible. When the clutch is actuated or closed, the two components accordingly rotate in the same direction at the same speed.

A brake is preferably to be understood in the description, in particular in the claims, as a switching element which is connected on one side to a fixed element, for example a housing, and on the other side to a rotatable element.

In the following, a brake that is not actuated is an open brake. This means that the rotating component is freely rotatable, i.e. the brake preferably has no influence on the speed of the rotating component. When the brake is actuated or closed, the speed of the rotatable component is reduced to a standstill, i.e. a fixed connection between the rotatable element and the stationary element can be established. Element and component are to be equated in this context. In principle, it is also possible to use switching elements which are closed in the non-actuated state and opened in the actuated state. Accordingly, the assignments between the function and the switching state of the switching states described above are to be understood in the opposite way. In the following exemplary embodiments with reference to the figures, an arrangement is initially used in which an actuated switching element is closed and an unactuated switching element is open.

A planetary gear set comprises a sun gear, a planet carrier or web and a ring gear. Planet gears are rotatably mounted on the planet carrier or web or planets which mesh with the toothing of the sun gear and / or the toothing of the ring gear.

In the following, a minus planetary gear set describes a planetary gear set with a planet carrier on which the planet gears are rotatably mounted, with a sun gear and with a ring gear, the toothing of at least one of the planet gears meshing with both the toothing of the sun gear and the toothing of the ring gear, whereby the ring gear and the sun gear rotate in opposite directions of rotation when the sun gear rotates with the planet carrier fixed.

A plus planetary gear set differs from the minus planetary gear set just described in that the plus planetary gear set has inner and outer planet gears which are rotatably mounted on the planet carrier. The teeth of the inner planet gears mesh on the one hand with the teeth of the sun gear and on the other hand with the teeth of the outer planet gears. The toothing of the outer planet gears also meshes with the toothing of the ring gear. As a result, the ring gear and the sun gear rotate in the same direction of rotation when the planet carrier is stationary.

By using planetary gear sets, particularly compact gearboxes can be realized, which gives great freedom in the arrangement of the gearbox in the vehicle.

The elements of a planetary gear set are understood in particular to be the sun gear, the ring gear, the planet carrier or web and the planet gears or the planets of the planetary gear set.

The shifting elements are particularly preferably selectively operable, that is to say individually and as required, so that different gears can be achieved by means of different transmission ratios between the input shaft and the output shaft. The higher the number of gears, the finer a gear gradation can be realized with a large gear spread and thus, for example, an internal combustion engine of a motor vehicle can be operated in an optimal speed range and thus as economically as possible. At the same time, this contributes to an increase in Driving comfort, since the internal combustion engine can preferably be operated at a low speed level. For example, noise emissions caused by the operation of the internal combustion engine are also reduced.

Furthermore, the switching elements can be designed such that energy is required for changing a switching state of the switching elements, but not for maintaining the switching state itself.

Switch elements which can be actuated as required, such as electromechanical switching elements or electromagnetic switching elements, are particularly suitable for this purpose. They are characterized, in particular in comparison to conventionally hydraulically actuated switching elements, by a particularly low and efficient energy requirement, since they can be operated almost without loss. In addition, it is advantageously possible to dispense with permanently maintaining a control pressure for actuating the conventional hydraulic switching elements, for example, or to apply the required hydraulic pressure permanently to the respective switching element in the switched state. In this way, for example, additional components such as a hydraulic pump can be dispensed with, insofar as these serve exclusively to control and supply the conventionally hydraulically actuated switching elements. If the supply of further components with lubricants does not take place via a separate lubricant pump, but via the same hydraulic pump, this can be dimensioned at least smaller. Any leaks at the oil transfer points of the hydraulic circuit, especially in the case of rotating components, are also eliminated. This also particularly preferably contributes to an increase in efficiency of the transmission in the form of a higher degree of efficiency.

When using switching elements of the above-mentioned type which can be actuated as required, it is particularly advantageous if they are easily accessible from the outside. Among other things, this has the advantage that the required switching energy can be supplied to the switching elements well. Switching elements are therefore particularly preferably arranged such that they are easily accessible from the outside. Easily accessible from the outside in the sense of the switching elements means that no further components are arranged between the housing of the transmission and the switching element, or that the switching elements are particularly preferably arranged on the drive shaft or on the output shaft.

The term "bindability" in the description, in particular in the claims, is to be understood to mean that, in the case of different geometrical positions, the same connection or binding of interfaces is ensured without individual connecting elements or shafts crossing.

The term "stationary gear ratio" is to be understood as the gear ratio which is realized by the gear ratio between the sun gear and the ring gear of the respective planetary gear set when the planet carrier or web is fixed.

Further advantageous embodiments, features and advantages of the invention are described in the subclaims.

According to claim 1, the transmission has at least one further third, fourth, fifth and / or sixth planetary gear set, wherein at least two of the further planetary gear sets, in particular geometrically, are arranged one behind the other in the transmission and / or at least two of the further planetary gear sets. In particular, the first planetary gear set can be arranged within the fourth planetary gear set and / or the fifth planetary gear set within the sixth planetary gear set. One advantage that can be achieved with the nested design is that the transmission can be made even more compact axially.

According to claim 1, a third planetary gear set is arranged between the second and fourth planetary gear sets, the sun gear of the third planetary gear set being connected to the housing in a fixed manner or being connectable to the housing by means of a fifth switching element. If a third planetary gear set is arranged between the two planetary gear sets, the number of possible gear stages that can be represented by the transmission is further increased.

The web of the third planetary gear set is expediently non-rotatably connected to the ring gear of the fourth planetary gear set, or the web of the third planetary gear set is connected to the sun gear of the fifth planetary gear set, or the web of the third planetary gear set can be connected to the sun gear of the first planetary gear set by means of a sixth switching element or by means of a seventh switching element can be connected to the ring gear of the fourth planetary gear set. Through the Switching elements for coupling the web of the third planetary gear set can also increase the number of possible gear stages that can be represented by the transmission.

According to claim 1, the webs of the second planetary gear set are rotatably connected to the ring gear of the third planetary gear set or the webs of the second planetary gear set can be connected to the ring gear of the third planetary gear set by means of an eighth shifting element. An advantage that can be achieved by a fixed connection of the webs of a planet gear set with the ring gear of another planet gear set is that the construction of the transmission is considerably simplified.

An electrical machine is expediently arranged, in particular for providing reverse gears through the transmission. On the one hand, the electrical machine can provide electrical traction support, on the other hand it can also be used to represent reverse gears, by ultimately causing the output shaft to reverse the direction of rotation when displaying a forward gear.

The sun gear of the fourth planetary gear set is advantageously connected to the housing or can be connected to the housing by means of a ninth switching element. In this way, the central element of the fourth planetary gear set, the sun gear, can, among other things, be firmly connected to the housing as required, or the structure of the transmission is simplified if the sun gear is arranged fixed to the housing.

The sun gear of the fourth planetary gear set can expediently be connected to the ring gear of the fourth planetary gear set by means of a tenth switching element. If a sun gear of a planetary gear set can be connected to the ring gear of the planetary gear set by means of a switching element, the number of possible gear stages that can be represented by the transmission is further increased.

The ring gear of the first planetary gear set is advantageously connected in a rotationally fixed manner to the sun gear of the first planetary gear set, can be connected to the housing by the third switching element and / or can be connected to the output shaft with the fourth switching element. If switching elements are provided for coupling the ring gear of the planetary gear set, then the number of possible ones that can be represented by the gearbox becomes Gear steps also increased further. In addition, the ring gear of the first planetary gear set can be flexibly connected to different further gear elements.

The fifth planetary gear set and the sixth planetary gear set are expediently arranged in a nested manner and form a reverse gear group, the reverse gear group being arranged at the output of the transmission and the sun gear of the fifth planetary gear set being connected in a rotationally fixed manner to the web of the first planetary gear set, and the web of the fifth planetary gear set can be connected to the housing by means of an eleventh shift element to represent at least one reverse gear, and the sun gear of the sixth planetary gear set can be connected to the housing by means of a twelfth shift element and can be connected to the web of the fifth planetary gear set by means of a thirteenth shift element. The reverse gear group thus formed can be easily integrated into an existing transmission. Furthermore, the nested arrangement of the fifth and sixth planetary gear sets allows the transmission to be made even more compact axially, which overall reduces the installation space for the transmission.

Advantageously, the fifth planetary gear set is arranged at the input of the transmission and the sun gear of the fifth planetary gear set is rotationally fixed to the drive shaft and the web of the fifth planetary gear set can be connected to the housing by means of an eleventh shift element for providing at least one reverse gear or can be provided by means of a further shift element at least one forward gear can be connected to the drive shaft. By providing the fifth planetary gear set at the input of the transmission, an upstream group is provided in a simple manner. The at least one reverse gear can be arranged as a turn set at the transmission input.

The first planetary gear set and the second planetary gear set expediently form a first partial transmission, and the first planetary gear set forms a second partial transmission together with the third planetary gear set and the fourth planetary gear set. The first planetary gear set provides a range group shared by both sub-transmissions, so that the installation space is also shared by the common one Use of the first planetary gear set in both sub-transmissions for the transmission can be reduced.

A countershaft is advantageously arranged, the countershaft having at least one countershaft and at least two gear planes, the first gear plane being connectable to the web of the third planetary gear set by means of a switching element and the second gear plane being in drive connection with the web of the first planetary gear set. A double gear jump can be achieved in a simple manner through the two gear planes of the countershaft.

A separating clutch is expediently arranged as a starting clutch, which in particular connects a drive motor to the drive shaft at the input of the transmission. The disconnect clutch can be used as a starting clutch, for example when a traction force is supported by an electrical machine, if the energy store of the electrical machine is empty or the electrical machine is too weak.

Advantageously, at least 14 forward gears and at least seven reverse gears can be represented by means of at least nine shift elements and at least two powershift elements, as well as six planetary gear sets.

Further important features and advantages of the invention emerge from the drawings and from the associated description of the figures with reference to the drawings.

Preferred embodiments and embodiments of the invention are shown in the drawings and are explained in more detail in the following description, the same reference numerals referring to the same or similar or functionally identical components or elements.

• Fig. 1a ein Getriebe gemäß einer ersten Ausführungsform der vorliegenden Erfindung;
• Fig. 1b ein Übersetzungsschema für ein Getriebe gemäß Fig. 1a;
• Fig. 1c eine Schaltmatrix für ein Getriebe gemäß der Fig. 1a;
• Fig. 2 ein Getriebe gemäß einer zweiten Ausführungsform der Erfindung;
• Fig. 3a ein Getriebe gemäß einer dritten Ausführungsform der vorliegenden Erfindung;
• Fig. 3b ein Übersetzungsschema für ein Getriebe gemäß Fig. 3a;
• Fig. 3c eine Schaltmatrix für ein Getriebe gemäß der Fig. 3a;
• Fig. 4a ein Getriebe gemäß einer vierten Ausführungsform der vorliegenden Erfindung;
• Fig. 4b ein Übersetzungsschema für ein Getriebe gemäß Fig. 4a;
• Fig. 4c eine Schaltmatrix für ein Getriebe gemäß der Fig. 4a;
• Fig. 5 ein Getriebe gemäß noch einer fünften Ausführungsform der vorliegenden Erfindung;
• Fig. 6a ein Getriebe gemäß einer sechsten Ausführungsform der vorliegenden Erfindung;
• Fig. 6b ein Übersetzungsschema für ein Getriebe gemäß Fig. 6a;
• Fig. 6c eine Schaltmatrix für ein Getriebe gemäß der Fig. 6a;
• Fig. 7a ein Getriebe gemäß einer siebten Ausführungsform der vorliegenden Erfindung;
• Fig. 7b ein Übersetzungsschema für ein Getriebe gemäß Fig. 7a;
• Fig. 7c eine Schaltmatrix für ein Getriebe gemäß der Fig. 7a;
• Fig. 8a ein Getriebe gemäß einer achten Ausführungsform der vorliegenden Erfindung;
• Fig. 8b ein Übersetzungsschema für ein Getriebe gemäß Fig. 8a;
• Fig. 8c eine Schaltmatrix für ein Getriebe gemäß der Fig. 8a;
• Fig. 9a ein Getriebe gemäß einer neunten Ausführungsform der vorliegenden Erfindung;
• Fig. 9b ein Übersetzungsschema für ein Getriebe gemäß Fig. 9a;
• Fig. 9c eine Schaltmatrix für ein Getriebe gemäß der Fig. 9a;
• Fig. 10 Getriebe gemäß einer zehnten Ausführungsform der vorliegenden Erfindung;
• Fig. 11 Getriebe gemäß einer elften Ausführungsform der vorliegenden Erfindung;
• Fig. 12a ein Getriebe gemäß einer zwölften Ausführungsform der vorliegenden Erfindung;
• Fig. 12b ein Übersetzungsschema für ein Getriebe gemäß Fig. 12a; und
• Fig. 12c eine Schaltmatrix für ein Getriebe gemäß der Fig. 12a;

Each show in schematic form

• Fig. 1a a transmission according to a first embodiment of the present invention;
• Fig. 1b a translation scheme for a transmission according Fig. 1a ;
• Fig. 1c a switching matrix for a transmission according to the Fig. 1a ;
• Fig. 2 a transmission according to a second embodiment of the invention;
• Fig. 3a a transmission according to a third embodiment of the present invention;
• Fig. 3b a translation scheme for a transmission according Fig. 3a ;
• Fig. 3c a switching matrix for a transmission according to the Fig. 3a ;
• Fig. 4a a transmission according to a fourth embodiment of the present invention;
• Fig. 4b a translation scheme for a transmission according Fig. 4a ;
• Fig. 4c is a switching matrix for a transmission according to the Fig. 4a ;
• Fig. 5 a transmission according to yet a fifth embodiment of the present invention;
• Fig. 6a a transmission according to a sixth embodiment of the present invention;
• Fig. 6b a translation scheme for a transmission according Fig. 6a ;
• Fig. 6c a switching matrix for a transmission according to the Fig. 6a ;
• Fig. 7a a transmission according to a seventh embodiment of the present invention;
• Fig. 7b a translation scheme for a transmission according Fig. 7a ;
• Fig. 7c a switching matrix for a transmission according to the Fig. 7a ;
• Fig. 8a a transmission according to an eighth embodiment of the present invention;
• Fig. 8b a translation scheme for a transmission according Fig. 8a ;
• Fig. 8c a switching matrix for a transmission according to the Fig. 8a ;
• Fig. 9a a transmission according to a ninth embodiment of the present invention;
• Fig. 9b a translation scheme for a transmission according Fig. 9a ;
• Fig. 9c a switching matrix for a transmission according to the Fig. 9a ;
• Fig. 10 Transmission according to a tenth embodiment of the present invention;
• Fig. 11 Transmission according to an eleventh embodiment of the present invention;
• Fig. 12a a transmission according to a twelfth embodiment of the present invention;
• Fig. 12b a translation scheme for a transmission according Fig. 12a ; and
• Fig. 12c a switching matrix for a transmission according to the Fig. 12a ;

Fig. 1a shows a transmission according to a first embodiment of the present invention.

In Fig. 1a Reference numeral 1 denotes a multi-stage transmission in planetary design. This in Fig.1a The multi-speed transmission 1 shown can be designed, for example, in the form of a double clutch transmission with seven gears comprising two direct drive (DD) gears. The term "direct drive" means in particular that the highest gear corresponds to a direct gear. Next is in Fig. 1a , as well as in the following Figures 2-12a only one gear half of the rotationally symmetrical gear is shown.

The transmission 1 has a total of eight shift elements A, B, C, D, E, F, K1, B2, one in the form of a clutch K1 and one in the form of a brake B2 and four planetary gear sets PG1, PG2, PG3 and PG4 . The six switching elements A, B, C, D, E and F form three double switching elements A / B, C / D and E / F, for example. Preferably, most or particularly preferred all switching elements of the transmission 1 are arranged accessible from the outside in a housing G for the transmission 1, so that they can be actuated from the outside, for example by means of shift forks or the like. This applies to all embodiments of the invention and in particular those in the Figures 1-12 described embodiments. In addition, the transmission 1 has, for example, a plurality of transmission shafts GW1, GW2 and GW3, the first transmission shaft GW1 forming the drive shaft ANW and the third transmission shaft GW3 the output shaft AW.

The general structure of the first planetary gear set PG1, the second planetary gear set PG2, the third planetary gear set PG3 and the fourth planetary gear set PG4 of the transmission 1 is described below. The planetary gear sets PG1, PG2, PG3, PG4 each have a sun gear 101, 102, 103, 104, which cooperates with at least one planet 111.1, 111.2, 112, 113, 114 for the transmission of force and torque. The first planetary gear set PG1 has two planets 111.1 and 111.2, the planet 111.1 being in engagement with the sun gear 101. On the radial outside of the respective planet 111.2, 112, 113, 114 of the first, second, third and fourth planetary gear sets PG1, PG2, PG3, PG4 there is in each case a ring gear 131, 132, 133, 134 into which the respective planet 111.2, 112, 113, 114 engages to transmit force and torque. The planets 111.1, 111.2, 112, 113, 114 are each rotatably mounted on a corresponding planet carrier 121.1, 121.2, 122, 123, 124.

In the case of the first planetary gear set PG1, its sun gear 101 is connected to the clutch K1. Furthermore, a first double switching element A / B is provided, which combines the two switching elements A and B. If the first switching element A is closed or actuated, the drive shaft ANW is connected to the clutch K1 and, if the clutch K1 is also actuated, the drive shaft ANW is correspondingly connected to the sun gear 101. If the second switching element B is closed or actuated, then the clutch K1 is connected to the housing G and, if the clutch K1 is additionally actuated, the housing G is correspondingly connected to the sun gear 101, so that the sun gear 101 is fixed to the housing. The ring gear 131 of the first planetary gear set PG1 is rotatably connected to the sun gear 104 of the fourth planetary gear set PG4. Here, the ring gear 131 and the sun gear 104 are each rotatably connected to the second gear shaft GW2. Furthermore, the first planet 111.1 of the first planetary gear set PG1 is rotatably mounted on the first carrier / planet carrier 121.1. The second planet 111.2 is on the second Bridge / planet carrier 121.2 rotatably mounted. The first web 121.1 and the second web 121.2 of the first planetary gear set PG1 are connected on the one hand to the drive shaft ANW or first transmission shaft GW1 and on the other hand to the ring gear 132 of the second planetary gear set PG2.

The planet 112 of the second planetary gear set PG2 is rotatably mounted on the web 122 of the second planetary gear set PG2. The sun gear 102 of the second planetary gear set PG2 can be connected to the housing G in a rotationally fixed manner via the brake B2. The web 122 of the second planetary gear set PG2 can be coupled to further gear elements by means of the second double switching element C / D. The second double switching element C / D combines the two switching elements C and D. The web 122 of the second planetary gear set PG2 can be connected to the second gear shaft GW2 or the sun gear 104 of the fourth planetary gear set PG4 by means of the third switching element C. Furthermore, the web 122 of the second planetary gear set can in turn be connected to the ring gear 133 of the third planetary gear set PG3 by means of the fourth switching element D.

The sun gear 103 of the third planetary gear set PG3 is connected to the housing G or fixed to the housing. The planet 113 of the third planetary gear set PG3 is rotatably mounted on the web 123 of the third planetary gear set PG3 and is connected in a rotationally fixed manner to the web 124 of the fourth planetary gear set PG4. As previously described, the ring gear 133 of the third planetary gear set PG3 can be connected to the web 122 of the second planetary gear set PG2 by means of the fourth switching element D.

The sun gear 104 of the fourth planetary gear set PG4 is rotatably connected to the ring gear 131 of the first planetary gear set PG1. In the embodiment in Fig. 1a For this purpose, the sun gear 104 of the fourth planetary gear set PG4 and the ring gear 131 of the first planetary gear set PG1 are rotatably connected to the second gear shaft GW2. The planet 114 of the fourth planetary gear set PG4 is rotatably mounted on the web 124 of the fourth planetary gear set PG4, the web 124 being connected in a rotationally fixed manner to the output shaft AW or the third gear shaft GW3. The ring gear 134 of the fourth planetary gear set PG4 can be connected to the housing G by means of the fifth shift element E of the double shift element E / F. If, on the other hand, the sixth switching element F is actuated or closed, the ring gear is 134 of the fourth planetary gear set PG4 connected to the output shaft AW or third gear shaft GW3.

The transmission 1, as in Fig. 1a is shown, has a first and second sub-transmission TG1 and TG2, each with a friction shift element, ie the clutch K1 and the brake B2, for power shifts. The friction shift elements K1 and B2 are distributed shift elements, so that the transmission 1 according to Fig. 1a does not have a typical double clutch, since no common drive shaft is provided for the clutch K1 and the brake B2.

The first sub-transmission TG1 comprises the first and fourth planetary gear sets PG1 and PG4 and the second sub-transmission TG2 the second, third and fourth planetary gear sets PG2, PG3 and PG4.

The first partial transmission TG1 has 2x2 = 4 translations, the first double shift element A / B switching two translations. The step change k is geometrically, for example, 1.31. The second switching element B switches a so-called underdrive ratio k ² , which can be provided by means of the first planetary gear set PG1. The drive takes place from the drive shaft ANW and the webs 111.1 and 111.2 of the first planetary gear set PG1 connected to it in a rotationally fixed manner. The output again takes place via the ring gear 131 of the first planetary gear set PG1 and the sun gear 104 of the fourth planetary gear set PG4 connected to it in a rotationally fixed manner. The sun gear 103 of the third planetary gear set PG3 is fixed to the housing, as previously described. There is a plus transmission here. Furthermore, a direct translation i = 1 can be switched by means of the first switching element A. The first planetary gear set PG1 is in block circulation. These two translations are doubled by the fourth planetary gear set PG4. Four gears can thus be represented. The fourth planetary gear set PG4 is a range group that is shared between the two partial transmissions TG1 and TG2. The drive shaft ANW runs through the first sub-transmission TG1 to the second sub-transmission TG2.

The second partial transmission TG2 comprises, as described above, the second, third and fourth planetary gear sets PG2, PG3 and PG4 and there are therefore 1x2 + 1 = 3 gear ratios. The third shift element C switches an underdrive ratio k ¹ for the second partial transmission TG2. The drive takes place via the ring gear 132 of the second planetary gear set PG2, which is rotatably connected to the two webs 121.1 and 121.2 of the first planetary gear set PG1 and the drive shaft ANW. The output takes place in turn via the web 122 of the second planetary gear set PG2, the sun gear 102 of the second planetary gear set PG2 being connectable to the housing G by means of the brake B2. This is used twice over the fourth planetary gear set PG4, ie there are 1x2 = 2 gear ratios. The fourth shift element D shifts a gear with the transmission ratio k ³ regardless of the range group that is formed by the fourth planetary gear set PG4. This gear is generated together by the second and third planetary gear sets PG2 and PG3. The second planetary gear set PG2 generates a translation k ¹ and the third planetary gear set PG3 generates a translation k ² . This results in the translation k ^{3 when connected in series} . This gear is therefore used twice by the fourth planetary gear set PG4. As a result, the fourth planetary gear set PG4 with the fifth switching element E and the sixth switching element F can be switched as load-free as a background circuit.

Fig. 1b shows a translation scheme for a transmission according to Fig. 1a .

In Fig. 1b is an example of a translation table for translations of the four planetary gear sets PG1-PG4 of the transmission according to Fig. 1a shown. A respective stationary gear ratio i0 and a respective gear ratio of the planetary gear set i_PG are given for the planetary gear sets PG1-PG4.

Fig. 1c shows a switching matrix for a transmission according to Fig. 1a .

In Fig. 1c is an exemplary shift matrix of the transmission according to Fig. 1a shown. In the in Fig. 1c shown shift matrix are only crosses for those of the switching elements, ie the switching elements AF, the clutch K1 and the brake B2, which are necessary for the respective of the forward gears V1-V7, and are actuated or closed in the respective gear. However, other shift elements can also be actuated or closed in order to preselect a gear in the other sub-transmission or to establish defined speed ratios on all shafts etc. These additional actuated or closed shift elements are then load-free. In the penultimate column of the shift matrix, the gear ratios i of the shifted forward gears V1-V7 are given as examples. In the last column of the Shift matrix, the resulting transmission ratio phi of the next lower gear to the relevant forward gear V1-V7 is again given.

An advantage of the gearbox as in Fig.1a is shown is that all switching elements are accessible from the outside. No pot penetrations are necessary for shift forks.

Such a powershift transmission would be incomplete without a reverse gear or R-gear for short. This in Fig. 1a and the corresponding one 1b and 1c The transmission shown therefore serves as the basis for different variants of reverse gears or R gears, as shown in the following 2a to 12a becomes clear.

The switching elements A-F can be synchronized, for example, conventionally in the form of individually synchronized switching elements or with a central synchronization for both sub-transmissions TG1 and TG2, e.g. by means of a gear brake and / or by means of one or more electrical machines or electrical machines.

Fig. 2 shows a transmission according to a second embodiment of the invention.

In Fig. 2 is another embodiment of the multi-speed transmission according to Fig. 1a shown. The multi-speed transmission 10 in Fig. 2a Its structure essentially corresponds to that of transmission 1 Fig. 1a , so that on the description of this in 1a-1c is referenced to avoid unnecessary repetitions.

The transmission 10 according to Fig. 2 differs from the transmission 1 according to Fig. 1a in that the third and fourth planetary gear sets PG3 and PG4 are arranged nested. The fourth planetary gear set PG4 is arranged radially and coaxially within the third planetary gear set PG3. The sun gear 103 of the third planetary gear set PG3 is firmly connected to the housing G. Furthermore, the ring gear 133 of the third planetary gear set PG3 can be connected to the carrier 122 of the second planetary gear set PG2 by means of the fourth switching element D. In addition, the ring gear 133 of the third planetary gear set PG3 can be connected to the sun gear 104 of the fourth planetary gear set PG4 by means of the third switching element C. The planet 113 of the third planetary gear set PG3 is rotatably mounted on the web 123 of the third planetary gear set PG3 and the web 123 of the third planetary gear set PG3 rotatably connected to the web 124 of the fourth planetary gear set PG4. The planet 114 of the fourth planetary gear set PG4 is rotatably arranged on the web 124 of the fourth planetary gear set PG4. The two webs 123 and 124 of the third and fourth planetary gear sets PG3 and PG4, which are non-rotatably connected to one another, are in turn non-rotatably connected to a third gear shaft GW3, here in the form of the output shaft AW. The sun gear 104 of the fourth planetary gear set PG4 is, as described above, non-rotatably connected to the second gear shaft GW2 and thus fixed to the ring gear 131 of the first planetary gear set PG1. The ring gear 134 of the fourth planetary gear set PG4 can be coupled by means of the third double switching element E / F. The third double switching element E / F combines the two switching elements E and F. The ring gear 134 of the fourth planetary gear set PG4 can be connected to the housing G by means of the fifth switching element E. If this is closed, the ring gear 134 and the sun gear 103 of the third planetary gear set PG3 are connected to the housing G and are thus fixed to the housing. The ring gear 134 of the fourth planetary gear set PG4 can be connected to the third gear shaft GW3 or the output shaft AW by means of the sixth shift element F.

The nesting of the third and fourth planetary gear sets PG3 and PG4 is possible because of a small amount of stationary gear ratio i0 of the outer third planetary gear set PG3. The stationary gear ratio i0_PG3 of the third planetary gear set PG3 is i0_PG3 = -1.42. That means a sun gear with a large diameter.

The friction switching elements, ie the clutch K1 and the brake B2, can be constructed in a further exemplary embodiment of the transmission according to FIG Fig. 2a can also be nested on the circumference of the first and second planetary gear sets PG1 and PG2. The advantage of nesting is that it saves axial installation space.

Fig. 3a shows a transmission according to a third embodiment of the invention.

In Fig. 3a is yet another embodiment of the multi-speed transmission according to Fig. 1a shown. The multi-speed transmission 10 in Fig. 3a corresponds essentially in its structure to the variant of the previous in Fig. 2 shown transmission 10, so that to the designs Fig. 2 and accordingly also to the 1a-1c referred becomes. This in Fig. 3a The transmission 10 shown can be designed, for example, in the form of a double clutch transmission with a 14-speed DD (Direct Drive, ie the highest gear is a direct gear) in a planetary design. The transmission is referred to below as the main transmission 1, expanded by a range group with three ranges (low, high and R).

The transmission 10 according to Fig. 3a differs from the transmission 10 according to FIG Fig. 2 in that an additional fifth and sixth planetary gear set PG5 and PG6 and three additional shifting elements R, H and L are arranged. The switching elements H and L are combined in the double switching element H / L.

The two additional planetary gear sets PG5 and PG6 are now connected in the following way: The web 124 of the fourth planetary gear set PG4 is rotatably connected to the sun gear 105 of the fifth planetary gear set PG5 by means of the third gear shaft GW3. Accordingly, the web 124 of the fourth planetary gear set PG4 is rotatably connected to the sun gear 105 of the fifth planetary gear set PG5. The fifth planetary gear set PG5 has the planet 115, which is rotatably mounted on a web 125 of the fifth planetary gear set PG5. The web 125 is also non-rotatably connected to a ring gear 136 of the sixth planetary gear set PG6. The sixth planetary gear set PG6 also has a planet 116 which is rotatably mounted on a web 126 of the sixth planetary gear set PG6. The web 126 of the sixth planet gear set PG6 is rotatably connected to a fourth gear shaft GW4, which e.g. the output shaft AW forms.

As described above, an additional seventh switching element R is provided. When actuated or closed, this seventh switching element R connects the web 125 of the fifth planetary gear set PG5 to the housing G. Furthermore, the fourth double switching element H / L is additionally provided. The web 125 of the fifth planetary gear set PG5 can be connected or coupled to the sun gear 106 of the sixth planetary gear set PG6 by means of the eighth switching element H. The sun gear 106 of the sixth planetary gear set PG6 can be connected to the housing G by means of the ninth switching element L.

The so-called range group, with which at least one reverse gear or R-gear can be represented, comprises the inner fifth planetary gear set PG5 and the outer one sixth planetary gear set PG6, as well as the three additional shifting elements L, H and R. Fig. 3a shown embodiment achieve a doubling of the number of gears of the main transmission 1 by one of the range groups L, H, R. The 7-8 shift, ie the shift from the seventh gear V7 to the eighth gear V8, is interrupted by traction. There is a change from L for "Low" to H for "High". This enables the transmission to be used in particular in trucks. The gear jump V7-V8, ie the gear jump from the seventh gear V7 to the eighth gear V8, can for example be chosen to be smaller because of the loss of speed during the traction-interrupted shift. All reverse gears or R gears can be power shifted with each other. Switching forwards / backwards using the switching elements L and R is not power switchable.

An advantage of this embodiment is that all switching elements A-F, as well as clutch K1 and brake B2, are accessible from the outside.

The addition of a range group, as exemplified in Fig. 3a is shown, is possible with all main transmission variants, which are described in the present application. The range group can provide at least one reverse gear.

Fig. 3b shows a translation scheme for a transmission according to Fig. 3a .

Fig. 3b shows an example of a translation table for translations of the six planetary gear sets PG1-PG6 of the transmission according to Fig. 3a . A respective stationary gear ratio i0 for the planetary gear sets PG1-PG6 and a respective ratio of the planetary gear set i_PG for the planetary gear sets PG1-PG4 are given.

Fig. 3c shows a switching matrix for a transmission according to Fig. 3a .

In Fig. 3c is an example of a shift matrix of the transmission according to Fig. 3a shown. In the in Fig. 3c shown shift matrix are only crosses for those of the switching elements, ie the switching elements AF, L, H and R, the clutch K1 and the brake B2, which are necessary for the respective of the forward gears V1-V14 and reverse gears R1-R7, and in this gear are operated or closed, otherwise they are open. The gear ratios are again exemplary in the penultimate column of the shift matrix i of the shifted forward gears V1-V14 and reverse gears R1-R7 specified. In addition, the resulting transmission ratio phi of the next lower gear to the relevant forward gear V1-V14 or reverse gear R1-R7 is specified in the last column of the shift matrix. By means of the gearbox Fig. 3a at least 14 forward gears and at least 7 reverse gears can be represented.

Fig. 4a shows a transmission according to a fourth embodiment of the present invention.

In Fig. 4a is a variant of the multi-speed transmission according to Fig. 2 shown. The multi-speed transmission 10 in Fig. 4a Its structure essentially corresponds to that of transmission 1 Fig. 2 , so that on the description of this in Fig. 2 , as well as accordingly 1a-1c is referenced to avoid unnecessary repetitions. This in Fig. 4a Transmission 10 shown is a variant of the 7-speed DD transmission with a block circulation of the third planetary gear set PG3.

The multi-speed transmission 10 according to Fig. 4a differs from the gearbox according to Fig. 2 in that the third planetary gear set PG3 in Fig. 4a can be connected to the sun gear 103 of the third planetary gear set PG3 by means of an additional seventh switching element J. In order to connect the sun gear 103 of the third planetary gear set PG3 to the housing, the additional eighth switching element K is also provided which, when it is actuated or closed, connects the sun gear 103 to the housing G. The additional fourth double shift element J / K enables block rotation of the third planetary gear set PG3 in all forward gears except the fourth forward gear. In the fourth forward gear, the fourth shift element D is closed and the force and torque flow is via the ratio provided by the third planetary gear set PG3. For block circulation on the third planetary gear set PG3, the seventh shifting element J is actuated or closed in all gears except the 4th forward gear.

In a further embodiment of the transmission, according to Fig. 4a instead of the third switching element C, the fourth switching element D can also be closed or remain closed. The block rotation always generates a gear ratio of 1. If the 4th forward gear is required, the sun gear 103 of the third planetary gear set PG3 are braked with the eighth switching element K. In yet another embodiment of the transmission, which is not shown, the seventh shift element J can also be designed such that it connects the sun gear 103 of the third planetary gear set PG3 to the web 123 of the third planetary gear set PG3. An advantage of the gearbox Fig. 4a it is that due to the block rotation on the third planetary gear set PG3, drag losses due to load-free rolling gears as well as rotating planet gears and their planet gear bearing are avoided with the third planetary gear set PG3.

Fig. 4b shows a translation scheme for a transmission according to Fig. 4a .

In Fig. 4b is an example of a shift matrix of the transmission according to Fig. 4a shown. In the in Fig. 4b shown shift matrix are only crosses for those of the switching elements, ie the switching elements AF, the clutch K1 and the brake B2, which are necessary for the respective of the forward gears V1-V7, and are actuated or closed in this gear. However, other shift elements can also be actuated or closed in order to preselect a gear in the other sub-transmission or to establish defined speed ratios on all shafts, etc. In the penultimate column of the shift matrix, the gear ratios i of the shifted forward gears V1-V7 are given by way of example. In the last column of the shift matrix, the resulting transmission ratio phi of the next lower forward gear to the relevant forward gear V1-V7 is again given. By means of the gearbox Fig. 4a at least 7 forward gears can be represented.

Fig. 5 shows a transmission according to a fifth embodiment of the present invention.

Here shows Fig. 5 a variant of the multi-speed transmission according to Fig. 1a . The multi-speed transmission 10 in Fig. 5 Its structure corresponds essentially to that of transmission 1 Fig. 1a , so that on the description of this in 1a-1c is referred.

The transmission 10 as in Fig. 5 is shown, in contrast to the transmission 1 according to FIG Fig. 1a . The second clutch K2 is in the Fig. 5 Embodiment shown in the power and torque flow between the Web 121.1 or 121.2 and the ring gear 132 of the second planetary gear set PG2. When actuated or closed, the second clutch K2 connects the two webs 121.1 and 121.2 of the first planetary gear set PG1, which are connected to one another in a rotationally fixed manner, with the ring gear 132 of the second planetary gear set PG2.

The force and torque flow via the second sub-transmission TG2 can instead of the brake B2 on the sun gear 102 of the second planetary gear set PG2, as in the transmission 1 according to Fig. 1a , in the embodiment in Fig. 5 can also be switched with the second clutch K2. The second clutch K2 connects the drive shaft ANW, which is connected in a rotationally fixed manner to the two webs 121.1 and 121.2 of the first planetary gear set PG1, with the input shaft of the partial transmission TG2 or the ring gear 132 of the second planetary gear set PG2.

There are differences in the design of the friction switching element, i.e. the second clutch K2, compared to a brake B2. There are different torque support factors and different differential speeds on the switching element. The corresponding shift matrix remains the same, only that instead of brake B2, clutch K2 must now be closed.

In a variant of the not shown in Fig. 5 shown transmission, the second clutch K2 is arranged between the web 122 of the second planetary gear set PG2 and the second double shift element C / D. There are then other torque support factors and different differential speeds on the respective switching element.

In yet another variant of the in Fig. 5 Gearbox shown, the first clutch K1 is arranged between the ring gear 131 of the first planetary gear set PG1 and the sun gear 104 of the fourth planetary gear set PG4, but still in terms of torque before the third switching element C. In this case, the first clutch K1 is arranged on the inside. Furthermore, a higher torque support factor would be generated.

Fig. 6a shows a transmission according to a sixth embodiment of the present invention.

In Fig. 6a 10 is a further embodiment based on the transmission 1 according to FIG Fig. 1a shown, the multi-speed transmission 10 in Fig. 6a For example, as an 8-speed DD (Direct drive, ie the highest gear is a direct gear) dual clutch transmission can be designed. The previous wheel set of the 7-speed DD gearbox, such as that in Fig. 1a is shown, is expanded with an additional fourth double shift element Y / H to an 8-speed DD transmission. The double switching element Y / H combines a seventh switching element Y and an eighth switching element H. Compared to the 7-speed DD transmission with seven forward gears, there is an additional short forward gear. The translation is provided by the second partial transmission TG2. The second, third and fourth planetary gear sets PG2, PG3 and PG4 work together for the new 1st forward gear, as also in the following shift matrix in Fig. 6c is shown.

As in Fig. 6a is shown, the web 122 of the second planetary gear set PG2 is rotatably connected to the ring gear 133 of the third planetary gear set. The sun gear 103 of the third planetary gear set PG3 can be connected to the housing G by means of the seventh switching element Y. The sun gear 103 of the third planetary gear set PG3 can in turn be coupled to the web 123 of the third planetary gear set PG3 by means of the eighth switching element H of the double switching element Y / H. The web 123 of the third planetary gear set PG3, when the third switching element C is actuated or closed, is connected to the second gear shaft GW2 and the sun gear 104 of the fourth planetary gear set PG4, which is connected in a rotationally fixed manner to the second gear shaft GW2. If, on the other hand, the fourth switching element D of the second double switching element C / D is actuated or closed, the web 123 of the third planetary gear set PG3 is connected to the web 124 of the fourth planetary gear set PG4, which in turn is connected in a rotationally fixed manner to the third gear shaft GW3 in the form of the output shaft AW is.

Fig. 6b shows a translation scheme for a transmission according to Fig. 6a .

Fig. 6b shows an example of a translation table for translations of the four planetary gear sets PG1-PG4 of the transmission according to Fig. 6a . Here is a respective stationary gear ratio i0 for the planetary gear sets PG1-PG4 and a respective one Translation of the planetary gear set i_PG for the planetary gear sets PG1-PG4 specified.

Fig. 6c shows a switching matrix for a transmission according to Fig. 6a .

In Fig. 6c is an exemplary shift matrix of the transmission according to Fig. 6a shown. In the in Fig. 6c The shift matrix shown are only crosses for those of the shift elements, ie the four double shift elements A / B, C / D, E / F and Y / H, the clutch K1 and the brake B2, which are necessary for the respective forward gears V1-V8 are and are actuated or closed in the respective gear. However, other shifting elements can also be actuated or closed in order to preselect a gear in the other sub-transmission or to establish defined speed ratios on all shafts etc. In the penultimate column of the shift matrix, the gear ratios i of the shifted forward gears V1-V8 are also given by way of example . In the last column of the shift matrix, the resulting transmission ratio phi of the next lower forward gear to the relevant forward gear V1-V8 is also given.

In a variant of the transmission, instead of the third shift element C, the fourth shift element D can also be closed at the 7th forward gear V7. In this case, the sixth switching element F is load-free.

Fig. 7a shows a transmission according to a seventh embodiment of the invention.

Fig. 7a represents a further embodiment based on the transmission Fig. 1a The multi-speed transmission 10 in Fig. 7a can be like the multi-speed transmission in Fig. 6a be designed as an 8-speed DD (Direct drive, ie the highest gear is a direct gear) dual clutch transmission. The previous wheel set of the 7-speed DD gearbox, such as that in Fig. 1a is shown, is expanded with the additional fourth double shift element Y / H to an 8-speed DD transmission. Compared to the 7-speed DD transmission, there is an additional short forward gear. The translation is provided by the second partial transmission TG2. The second, third and fourth planetary gear sets PG2, PG3 and PG4 work together for the new 1st forward gear, as also in the following shift matrix in Fig. 7c is shown.

The gearbox like it in Fig. 7a is shown, has a different arrangement of the third and fourth double switching elements C / D and Y / H, compared to that previously in Fig. 6a shown transmission. The web 123 of the third planetary gear set PG3 is connected to the sun gear 104 of the fourth planetary gear set PG4 when the seventh switching element Y is actuated or closed. The sun gear 104 is connected in a rotationally fixed manner to the ring gear of the first planetary gear set PG1 via the second gear shaft GW2. If, on the other hand, the eighth switching element H of the double switching element Y / H is actuated or switched, the web 123 of the third planetary gear set PG3 is connected to the web 124 of the fourth planetary gear set PG4. This web 124 is in turn non-rotatably connected to the third gear shaft GW3, here in the form of the output shaft AW.

Fig. 7b shows a translation scheme for a transmission according to Fig. 7a .

In Fig. 7b is an example of a translation table for translations of the four planetary gear sets PG1-PG4 of the transmission according to Fig. 7a shown. A respective stationary gear ratio i0 for the planetary gear sets PG1-PG4 and a respective ratio of the planetary gear set i_PG for the planetary gear sets PG1-PG4 are given.

Fig. 7c shows a switching matrix for a transmission according to Fig. 7a .

In Fig. 7c is an example of a shift matrix of the transmission according to Fig. 7a shown. In the in Fig. 7c The shift matrix shown are only crosses for those of the shift elements, ie the four double shift elements A / B, C / D, E / F and Y / H, the clutch K1 and the brake B2, which are necessary for the respective forward gears V1-V8 and are actuated or closed in this gear. However, further shift elements can also be actuated or closed in order to preselect a gear in the other sub-transmission or to establish defined speed ratios on all shafts etc. The gear ratio i of the shifted forward gears V1-V8 are given as an example in the penultimate column of the shift matrix. In the last column of the shift matrix, the resulting transmission ratio phi of the next lower forward gear to the relevant forward gear V1-V8 is also given. By means of the gearbox Fig. 7a at least 8 forward gears can be represented.

Fig. 8a shows a transmission according to an eighth embodiment of the invention.

In Fig. 8a 10 is yet another embodiment of a transmission 10 based on the transmission 1 of FIG Fig. 1a shown. The multi-speed transmission 10 in Fig. 8a can, like the multi-speed transmission in Fig. 1a , as a 7-speed DD (Direct drive, ie the highest gear is a direct gear) double clutch transmission and more precisely, for example, as an automated manual transmission (AMT).

The multi-speed transmission 10 according to Fig. 8a differs from the transmission 1 according to Fig. 1a in that the two load switching elements K1 and B2 in Fig. 1a or correspondingly the load switching element K2 in Fig. 5 be replaced by fixed connections. This creates a non-power shiftable, automated manual transmission (AMT). Shifting is then only possible with interruptions in tractive power. In addition, a separating clutch K0 is provided as a conventional starting clutch.

As in Fig. 8a is shown, the sun gear 101 of the first planetary gear set PG1 can be coupled directly by means of the first double switching element A / B instead of as in FIG Fig. 1a to provide a clutch K1 for connecting the sun gear 101 to the first double switching element A / B. Furthermore, the sun gear 102 of the second planetary gear set PG2 is connected to the housing G and is thus fixed to the housing instead of as in FIG Fig. 1a to be connectable to the housing G by means of the brake B2. When a clutch K0 is actuated or closed, a drive motor is connected to the input shaft of the transmission 1 by means of a clutch. The input shaft or first gear shaft GW1 is rotatably connected to the two webs 111.1 and 111.2 of the first planetary gear set PG1.

With the gearbox according to Fig. 8a the reverse gear or R-gear is missing. An additional assembly can therefore be provided, for example a combination with a range group with integrated reverse gear or a reverse gear stage.

In the Fig. 8a The embodiment of the transmission shown has the advantage of an inexpensive transmission. Furthermore, the efficiency can be increased by eliminating the load switching elements. There is also a use of the main transmission possible as a modular system, e.g. for a powershift transmission (DCT-like) or as an automated manual transmission with interruption in tractive power.

In a variant of the not shown in Fig. 8a shown transmission is arranged instead of the fixed sun gear 103 of the third planetary gear set PG3, a common component of the sun gear 103 of the third planetary gear set PG3 and the ring gear 134 of the fourth planetary gear set PG4. This is particularly useful when nesting the third and fourth planetary gear sets PG3 and PG4 and has the advantage that block rotation is possible with the third planetary gear set PG3 when the sixth shift element F is closed. In this case, there are no bearing losses in the planet 113 of the third planetary gear set PG3. A preparatory background shift through the fifth shift element E and the sixth shift element F is no longer possible, which causes a longer shift duration from the 4th forward gear V4 to the 5th forward gear V5. In the following Fig. 8c Switching matrix shown, the fifth shift element E must remain closed in the 4th forward gear V4 in order to keep the sun gear 103 fixed to the housing.

Fig. 8b shows a translation matrix for a transmission according to Fig. 8a .

Fig. 8b shows an example of a translation table for translations of the four planetary gear sets PG1-PG4 of the transmission according to Fig. 8a . A respective stationary gear ratio i0 for the planetary gear sets PG1-PG4 and a respective ratio of the planetary gear set i_PG for the planetary gear sets PG1-PG4 are given.

Fig. 8c shows a switching matrix for a transmission according to Fig. 8a .

In Fig. 8c is an example of a switching matrix of the transmission 10 according to Fig. 8a shown. In the in Fig. 8c shift matrix shown are only crosses for those of the shift elements, ie the three double shift elements A / B, C / D and E / F and the clutch K0, which are necessary for the respective of the forward gears V1-V7 and are actuated or in this gear getting closed. In the penultimate column of the shift matrix, the gear ratios i of the shifted forward gears V1-V7 are given as examples. In addition, in the last column of the shift matrix is the resulting transmission ratio phi of the next lower forward gear to the gear in question Forward gear V1-V7 specified. By means of the gearbox Fig. 8a at least 7 forward gears can be represented. Fig. 9a shows a transmission according to a ninth embodiment of the present invention.

In Fig. 9a a further multi-speed transmission 10 is shown. The multi-speed transmission 10 represents a variant of the transmission 10 according to Fig. 2 The structure of the multi-stage transmission 10 essentially corresponds to that of the transmission Fig. 2 , so that regarding the structure of the multi-speed transmission 10 toward the description Fig. 2 and related to the description of the 1a-1c is referred. This in Fig. 9a The shown transmission 10 is a hybrid transmission, which represents a variant of the 7-speed DD transmission in planetary construction and has an additional electrical traction support by means of an electrical machine EM.

The multi-speed transmission 10 according to Fig. 9a differs from the transmission 10 according to FIG Fig. 2 in that the first clutch K1 is omitted. Instead, a separating clutch K0, as previously in Fig. 8a intended. The separating clutch K0 serves as a conventional starting clutch and connects a drive motor or internal combustion engine to the input shaft of the transmission 10. The drive motor is coupled to the first partial transmission TG1 in the exemplary embodiment in FIG Fig. 9a solely by means of the first and second switching elements A and B. These are combined, for example, in the first double switching element A / B.

Furthermore, the brake B2 in Fig. 1a or the corresponding clutch K2 in Fig. 5 , in the in Fig. 9a shown transmission variant replaced by an additional shift element X. If the additional switching element X is actuated or closed, it connects the input shaft and the webs 111.1, 111.2 of the first planetary gear set PG1 connected to it in a rotationally fixed manner with the ring gear 132 of the second planetary gear set PG2. The drive motor is coupled to the second partial transmission TG2. In addition, an electrical machine EM is arranged for a load circuit. Here, traction is always supported by the electrical machine EM via the second partial transmission TG2. When shifting in the second sub-transmission TG2, the drive motor receives a tractive force via the first sub-transmission TG1. This means that there is only an alternation between the first sub-transmission TG1 and the second sub-transmission TG2.

A reverse gear or R gear or reverse gear stage can be dispensed with by using the electric machine EM for driving backwards, in particular by rotating it backwards in the forward gear.

The friction clutch K0 is optional. It can be provided as a starting clutch if the electrical machine EM is too weak or the energy store or electrical store of the electrical machine EM is empty. The separating clutch K0 is used to open gear synchronization. The shift then takes place as in the case of an automated manual transmission in the first partial transmission TG1. The second sub-transmission TG2, i.e. the second double switching element C / D is always synchronized by the speed control of the electrical machine EM.

Fig. 9b shows a translation scheme for a transmission according to Fig. 9a .

In Fig. 9b is an example of a translation table for translations of the four planetary gear sets PG1-PG4 of the transmission according to Fig. 9a shown. A respective stationary gear ratio i0 for the planetary gear sets PG1-PG4 and a respective ratio of the planetary gear set i_PG for the planetary gear sets PG1-PG4 are given.

Fig. 9c shows a switching matrix for a transmission according to Fig. 9a .

In Fig. 9c is an example of a switching matrix for a transmission according to Fig. 9a shown. In the in Fig. 9c shown switching matrix are only crosses for those of the switching elements, ie the three double switching elements A / B, C / D, E / F and the additional switching element X and the clutch K0, which are necessary for the respective of the forward gears V1-V7 and in this gear are operated or closed. In the penultimate column of the shift matrix, the gear ratios i of the shifted forward gears V1-V7 are given as examples. In addition, the resulting transmission ratio phi of the next lower forward gear to the relevant forward gear V1-V7 is specified in the last column of the shift matrix. By means of the gearbox Fig. 9a at least 7 forward gears V1-V7 can be represented.

Fig. 10 shows a transmission according to a tenth embodiment of the present invention.

Fig. 10 shows yet another multi-stage transmission 10. The multi-stage transmission 10 represents a further variant of the transmission 1 according to FIG Fig. 1a The structure of the multi-stage transmission 10 essentially corresponds to that of the transmission 1 according to Fig. 1a , so that regarding the structure of the multi-speed transmission 10 to the description in 1a-1c is referred. The transmission 10 in Fig. 10 represents a variant with at least one reverse gear or reverse gear stage as a PG5 turning set at the transmission input.

The transmission 10 according to the embodiment in Fig. 10 has in contrast to the multi-speed transmission 1 according to Fig. 1a an additional fifth planetary gear set PG5 and two additional shift elements V and R, which are combined, for example, in a double shift element V / R. If the switching element R is actuated, it connects the web 125 of the fifth planetary gear set PG5 to the housing G, so that the web 125 is fixed to the housing in order to provide at least one reverse gear. If, on the other hand, the switching element V is actuated, it connects the web 125 of the fifth planetary gear set PG5 to the drive shaft ANW and the sun gear 105 of the fifth planetary gear set PG5, which is non-rotatably connected to the drive shaft ANW, for a forward gear.

To represent a forward gear of the transmission 10, the switching element V is always actuated or closed, and to represent a reverse gear of the transmission 10, the switching element R is always actuated or closed. The reverse gears are shorter than the corresponding forward gears (factor i0 of the fifth planetary gear set PG5). In the short reverse gears, it may be necessary to limit the torque of the drive motor, because otherwise the reverse gear would be relevant for the design of the transmission due to the moment load. The short reverse gears prove to be advantageous for sensitive reverse maneuvering. A low driving speed is generated when the drive motor is idling with the clutch closed. The reverse gears are also power shiftable with each other.

Fig. 11 shows a transmission according to an eleventh embodiment of the present invention.

In Fig. 11 another multi-speed transmission 10 shown, which according to a variant of the transmission 1 Fig. 1a represents. The multi-speed transmission 10 corresponds in its Construction essentially according to the transmission 1 Fig. 1a , so that regarding the structure of the multi-speed transmission 10 to the description in 1a-1c is referred. This in Fig. 11 The transmission 10 shown represents a variant with a reverse gear as a PG5 reversing set within the partial transmission TG2.

The transmission 10 according to the embodiment in Fig. 11 differs from the multi-speed transmission 1 according to Fig. 1a in that it has an additional fifth planetary gear set PG5 and two additional shift elements V and R, which are combined, for example, in a fourth double shift element V / R. The fifth planetary gear set PG5 is arranged as a reversing set for the reverse gear within the second partial transmission TG2. The sun gear 105 of the fifth planetary gear set PG5 is rotatably connected to the web 122 of the second planetary gear set PG2. The planet 115 of the fifth planetary gear set PG5 is rotatably mounted on a web 125 of the fifth planetary gear set PG5. The web 125 can also be coupled by means of the fourth double switching element V / R. To provide a reverse gear, the web 125 of the fifth planetary gear set PG5 can be connected to the housing G by means of the eighth switching element R, so that the web 125 is fixed to the housing. To provide a forward gear, the web 125 of the fifth planetary gear set PG5 can be connected to the sun gear 105 of the fifth planetary gear set PG5 by means of the seventh shifting element V.

Furthermore, the ring gear 135 of the fifth planetary gear set PG5 can be coupled by means of the second double switching element C / D. If the third switching element C is actuated, it connects the ring gear 135 to the second gear shaft GW2 and the sun gear 104 of the fourth planetary gear set PG4, which is non-rotatably connected to the second gear shaft GW2. If, on the other hand, the fourth switching element D is actuated, it connects the ring gear 135 to the ring gear 133 of the third planetary gear set PG3.

In the forward gear of the transmission 1, the switching element V is always actuated or closed and in the reverse gear, the switching element R is always actuated or closed. The reverse gears are shorter than the corresponding forward gears of the second partial transmission TG2 (factor i0 of the fifth planetary gear set PG5). The reverse gears are also not power shiftable with each other. The change between forward and reverse gears, on the other hand, can be powershifted if in the first Sub gearbox TG1 a forward gear is selected and a reverse gear is selected in the second sub gear TG2. This is advantageous for dynamic reversing or rocking out of a trough.

Fig. 12a shows a transmission according to a twelfth embodiment of the present invention.

In Fig. 12a is yet another variant of the multi-speed transmission according to Fig. 1a shown. The structure of the multi-speed transmission 10 essentially corresponds to that of the transmission 1 Fig. 1a , so that regarding the structure of the multi-speed transmission 10 to the description in the 1a-1c is referred.

This in Fig. 12a The illustrated transmission 10 can be designed, for example, as a 7-speed transmission DD (Direct Drive). The transmission 10 differs from the transmission 1 according to FIG Fig. 1a in that there are only three planetary gear sets, here the first, second and fourth planetary gear sets PG1, PG2 and PG4. The third planetary gear set PG3, on the other hand, is omitted. Instead, a countershaft VG3 is provided with a countershaft VW1 and two gear planes, in particular in the form of spur gear stages I u, II.

The translation of k ² , ie a double gear shift, previously provided by the third planetary gear set PG3 is now realized by the two gear planes I and II of the countershaft gear VG3. The gear ratio of the reduction gear VG3 is similar to that of the third planetary gear set PG3, for example 1.7 over both gear planes I and II. The gear shafts GW1, GW2, GW3 can be brought into drive connection selectively via the two wheel planes I, II and six shift elements A, B, C, D, E and F, and the clutch K1 as a further shift element. The first gear plane I is connected to the sun gear 104 or the gear shaft GW2 when the fourth switching element D is actuated or closed. The second gear plane II is in turn always coupled to the web 124 of the fourth planetary gear set PG4 or the gear shaft GW3, which forms the output shaft AW. If the third switching element C of the double switching element C / D is actuated, it connects the web 122 of the second planetary gear set PG2 to the second gear shaft GW2 or the sun gear 104 of the fourth planetary gear set PG4, which is connected in a rotationally fixed manner to the gear shaft GW2.

An advantage of the gearbox Fig. 12a is that the third planetary gear set PG3 is omitted. The stationary gear ratio i0 was in the extreme range. As a result, a higher gear jump and overall a higher spread can be achieved. By eliminating the third PG3 planetary gear set, the associated bearing losses are also eliminated. Since the webs / planet carriers of the third planetary gear set PG3 have to be small, which means that they have to have an extremely small stationary gear ratio i0, high bearing speeds result.

The third and fourth switching elements C and D and the second double switching element C / D can be designed as a conventional switching element. This means that a central element is connected to a left neighbor or a right neighbor. This is particularly space-saving.

This in Fig.12a countershaft VG3 shown can also be designed in a construction, not shown, with two countershafts. The division of power is similar to that of a planetary gear with a fixed web. It is advantageous that the radial forces on the main shaft can be compensated here.

Fig. 12b shows a translation scheme for a transmission according to Fig. 12a .

In Fig. 12b is an example of a translation table for translations of the three planetary gear sets, ie here the first, second and fourth planetary gear sets PG1, PG2 and PG4 of the transmission 10 according to Fig. 12a shown. A respective stationary gear ratio i0 for the planetary gear sets PG1, PG2 and PG4 and a respective ratio of the planetary gear set i_PG for the planetary gear sets PG1, PG2 and PG4 are specified. For the countershaft transmission VG3, the translation of the countershaft transmission VG3 i_VG3 is also specified.

Fig. 12c shows a switching matrix for a transmission according to the Fig. 12a .

In Fig. 12c is a shift matrix for a transmission according to Fig. 12a shown. In the in Fig. 12c shown shift matrix are only crosses for those of the shift elements, ie the six shift elements AF, the brake B2 and the clutch K1, which are necessary for the respective of the forward gears V1-V7 and are actuated or closed in this gear. In the penultimate column of the shift matrix, the gear ratios i of the shifted forward gears V1-V7 are given as examples. Furthermore the resulting transmission ratio phi of the next lower forward gear to the relevant forward gear V1-V7 is given in the last column of the shift matrix. By means of the gearbox Fig. 12a at least 7 forward gears can be represented.

In a further variant, not shown, of the transmission according to Fig. 12a If the bindability permits, the minus planetary gear set is replaced by a plus planetary gear set. In order to provide a similarly desired translation, for example, the connection is adapted accordingly, ie the web and the ring gear are interchanged.

In a further variant, not shown, of the transmission according to Fig. 12a a planetary gear stage is replaced by a countershaft. This is not only possible, for example, for the third planetary gear set PG3, as in Fig. 12a is shown, but also for example for the second planetary gear set PG2.

In another variant of the transmission, not shown, according to Fig. 12a the reverse gear is provided as a spur gear stage, for example through a further gear plane in the countershaft variant of the third planetary gear set PG3.

In yet another variant, not shown, of the transmission according to Fig. 12a the two powershift elements K1 and K2 (or B2) are eliminated as in the variant of the automated manual transmission AMT in Fig. 7a . The first and second double shift elements A / B and C / D are then designed as load shift elements for the variants of the 7-speed transmission DD. This results in powershift transmissions with four powershift elements and a shared group, ie the fourth planetary gear set PG4, which is preselected without load with positive power shift elements E / F.

In summary, the present invention offers the advantages, among other things, that the transmission is compact, which results in lower manufacturing costs and lower weight of the transmission. In addition, the gearbox offers a good range of ratios, low inertia masses and a high power density. Furthermore, the present invention offers a high number of gears.

Furthermore, the shifting elements in the previously described embodiments of the invention can be actuated simply, since most or particularly preferably all shifting elements of the transmission are provided in the transmission that are accessible from the outside, in particular from the outside by shift forks.

Reference numerals

1, 10

transmission

GW1, GW2, GW3, GW4

Gear shaft

APP

drive shaft

AW

Output shaft

G

casing

PG1, PG2, PG3, PG4, PG5, PG6

Planetary gear set

101, 102, 103, 104, 105, 106

Sun gear

111.1, 111.2, 111, 112, 113, 114, 115, 116

planet

121.1, 121.2, 122, 123, 124, 125, 126

Bridge / planet carrier

131, 132, 133, 134, 135, 136

Ring gear

VG3

Gear

VW1

Countershaft

I, II

Wheel plane

i0

Stationary gear ratio

i_PG

Translation of the planetary gear set

i_VG3

Gear ratio transmission

k

Gang jump

A, B, C, D, E, F, H, J, K, L, V, R, X, Y

Switching element

K1, K2, K0

clutch

EM

electrical machine

V1, V2, V3, V4, V5, V6, V7, V8, V9, V10

Forward gear

V11, V12, V13, V14 R1, R2, R3, R4, R5, R6, R7

Reverse gear

Claims (11)

1. Transmission (1, 10), in particular multi-stage transmission, for a motor vehicle, comprising a housing (G), a drive shaft (ANW), an output shaft (AW), at least two planetary gear sets (PG1, PG4), wherein the first planetary gear set (PG4) comprises a sun gear (104), at least one planet (114), a carrier (124) and a ring gear (134), and multiple shift elements (A-F, H, J, K, L, V, R, X, Y) and a second planetary gear set (PG1) with a sun gear (101), at least one planet (111.1, 111.2 and a ring gear (131), wherein a sun gear (101) of the second planetary gear set (PG1) is connectable by means of at least one first shift element (K1, B) to the housing (G) and is connectable by means of a second shift element (A) to the drive shaft (ANW), and in that the ring gear (134) of the first planetary gear set (PG4) is connectable by means of a third shift element (E) to the housing (G) and by means of a fourth shift element (F) to the carrier (124) of the first planetary gear set (PG4), and in that the sun gear (104) of the first planetary gear set (PG4) and the ring gear (131) of the second planetary gear set (PG1) are connected rotationally conjointly to one another, and in that the majority, in particular all, of the shift elements (A, B, E, F, K1) are arranged in the housing (G) so as to be accessible from the outside, characterized in that the second planetary gear set (PG1) has at least two intermeshing planets (111.1, 111.2) and two carriers (121.1, 121.2) which are connected rotationally conjointly to one another, on which carriers in each case one of the two intermeshing planets (111.1, 111.2) is rotatably mounted, and in that the carriers (121.1, 121.2) of the second planetary gear set (PG1) are connected rotationally conjointly to the drive shaft (ANW), and the carrier (124) of the first planetary gear set (PG4) is connected rotationally conjointly to the output shaft (AW), wherein the transmission has at least one further third, fourth, fifth and/or sixth planetary gear set (PG2, PG3, PG5, PG6), wherein at least two of the planetary gear sets (PG1, PG2, PG3, PG4, PG5, PG6) are arranged one behind the other in the transmission (1, 10) and/or at least two of the planetary gear sets (PG3, PG4; PG5, PG6) are arranged in nested fashion, wherein the third planetary gear set (PG2) is arranged between the second and fourth planetary gear sets (PG1, PG3), wherein a sun gear (102) of the third planetary gear set (PG2) is connected fixedly to the housing (G) or is connectable by means of a fifth shift element (B2, C) to the housing (G), wherein the carriers (111.1, 111.2) of the second planetary gear set (PG1) are connected rotationally conjointly to a ring gear (132) of the third planetary gear set (PG2), or the carriers (111.1, 111.2) of the second planetary gear set (PG1) are connectable to the ring gear (132) of the third planetary gear set (PG2) by means of an eighth shift element (X).
2. Transmission according to Claim 1, characterized in that a carrier (122) of the third planetary gear set (PG2) is connected rotationally conjointly to a ring gear (133) of the fourth planetary gear set (PG3), the carrier (122) of the third planetary gear set (PG2) is connected to a sun gear (105) of the fifth planetary gear set (PG5), the carrier (122) of the third planetary gear set (PG2) is connectable by means of a sixth shift element (C) to the sun gear (104) of the first planetary gear set (PG4) and/or is connectable by means of a seventh shift element (D) to the ring gear (133) of the fourth planetary gear set (PG3).
3. Transmission according to either of Claims 1 and 2, characterized in that an electric machine (EM) is provided, in particular for providing reverse gear ratios through the transmission (1, 10).
4. Transmission according to any of Claims 1 to 3, characterized in that a sun gear (103) of the fourth planetary gear set (PG3) is connected to the housing (G) or is connectable by means of a ninth shift element (K, Y) to the housing (G).
5. Transmission according to any of Claims 1 to 4, characterized in that a sun gear (103) of the fourth planetary gear set (PG3) is connectable by means of a tenth shift element (J) to a ring gear (133) of the fourth planetary gear set (PG3).
6. Transmission according to any of Claims 1 to 5, characterized in that the ring gear (134) of the first planetary gear set (PG4) is connectable by means of the fourth shift element (F) to the output shaft (AW).
7. Transmission according to any of Claims 1 to 6, characterized in that the fifth planetary gear set (PG5) and the sixth planetary gear set (PG6) are arranged in nested fashion and form a reverse gear ratio group, wherein the reverse gear ratio group is arranged at the output of the transmission (1), and wherein the sun gear (105) of the fifth planetary gear set (PG5) is connected rotationally conjointly to the carrier (124) of the first planetary gear set (PG4), and a carrier (125) of the fifth planetary gear set (PG5) is connectable by means of an eleventh shift element (R), for realizing at least one reverse gear ratio (R1, R2, R3, R4, R5, R6, R7), to the housing (G), and wherein a sun gear (106) of the sixth planetary gear set (PG6) is connectable by means of a twelfth shift element (L) to the housing (G) and is connectable by means of a thirteenth shift element (H) to the carrier (125) of the fifth planetary gear set (PG5) .
8. Transmission according to any of Claims 1 to 7, characterized in that the first planetary gear set (PG4) and the second planetary gear set (PG1) form a first sub-transmission (TG1), and in that the first planetary gear set (PG4) together with the third planetary gear set (PG2) and the fourth planetary gear set (PG3) form a second sub-transmission (TG2).
9. Transmission according to any of Claims 1 to 8, characterized in that a countershaft arrangement (VG3) is provided, wherein the countershaft arrangement (VG3) has at least one countershaft (VW1) and at least two gear planes (I, II), wherein the first gear plane (I) is connectable by means of a shift element (D) to a carrier (122) of the third planetary gear set (PG3) and the second gear plane (II) has a drive connection to the carrier (124) of the first planetary gear set (PG4).
10. Transmission according to any of Claims 1 to 9, characterized in that a separating clutch (K0) is provided as launch clutch, which separating clutch in particular connects a drive engine to the drive shaft (ANW) at the input of the transmission (1).
11. Motor vehicle, in particular a passenger motor vehicle or motor truck, having a transmission (1) according to any of Claims 1 to 10.

Images